CN103542058B - Frictional infinitely variable speed device with double-intermediate-roller steering reducing mechanism - Google Patents
Frictional infinitely variable speed device with double-intermediate-roller steering reducing mechanism Download PDFInfo
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- CN103542058B CN103542058B CN201310480738.8A CN201310480738A CN103542058B CN 103542058 B CN103542058 B CN 103542058B CN 201310480738 A CN201310480738 A CN 201310480738A CN 103542058 B CN103542058 B CN 103542058B
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- roller
- intermediate roller
- shaft
- frictional disk
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
- F16H37/12—Gearings comprising primarily toothed or friction gearing, links or levers, and cams, or members of at least two of these types
-
- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02K—DYNAMO-ELECTRIC MACHINES
- H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
- H02K7/10—Structural association with clutches, brakes, gears, pulleys or mechanical starters
- H02K7/116—Structural association with clutches, brakes, gears, pulleys or mechanical starters with gears
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Power Engineering (AREA)
- Mechanical Engineering (AREA)
- Friction Gearing (AREA)
Abstract
The invention discloses a steering reducing infinitely variable speed mechanism with double intermediate rollers. The mechanism comprises an input shaft, an intermediate shaft, a master pin, a first intermediate roller, a second intermediate roller and an output shaft, and a pair of intermediate rollers with viscoelastic behavior is adopted as the first intermediate roller and the second intermediate roller. The intermediate rollers are enabled to deviate laterally to change radial positions thereof under the action of lateral force so as to regulate the speed ratio. The mechanism has the advantages that contact radius of a high-friction-coefficient driving wheel is controlled to be changed smoothly and continuously under the conditions of low resistance and low wear, the structure is simple, infinitely variable speed control is simplified, and bearing capacity of a frictional infinitely variable transmission is improved.
Description
Technical field
The invention belongs to mechanical transmission fields are and in particular to a kind of have the friction-type that double intermediate rollers turn to diameter changing mechanism
Stepless speed change device.
Background technology
Mechanical stepless speed change mechanism is a kind of continuously adjustable mechanical driving device of gear ratio, is widely used in all kinds of machineries
In equipment, there is various mechanism type.As inclined disc type in shifting roller tray type, cone disc annular disc type, optical axis, roller tray type, arc
Conical ring disc type etc..Frictional drive is the common mechanism pattern of mechanical stepless transmission, as common metal band type stepless speed variator
（VDT-CVT）.Slip gear utilizes the frictional force drive motion and power between certain positive pressure lower transmission component, its
Transmission frictional force（Torque）Ability depend on the coefficient of friction of driving member contact surface and normal pressure.Certain normal pressure condition
Under, the coefficient of friction increasing frictional drive wheel surface contact position is the important way improving frictional variable speed mechanism bearing capacity
Footpath.But existing frictional variable speed mechanism, if the coefficient of friction between its driving member takes higher value, changes in transmission process
Become the frictional resistance that drive effective CONTACT WITH FRICTION radius is realized overcoming needed for infinitely variable speeds, and consequent driving member connects
Tactile surface abrasion all will be increased dramatically.So, existing frictional variable speed mechanism actually all can only select coefficient of friction
Less and metal type frictional drive part that surface abrasion resistance is higher（Metal type drive or transmission belt）, or even also need to pass
Filling traction lubricating oil at moving part CONTACT WITH FRICTION（TractionOil）, lead to its bearing capacity to be very limited.
Therefore, in order to improve the bearing capacity of friction type stepless speed changer, searching is needed to adapt to great friction coefficient condition
Novel stepless speed change mechanism.
Patent 20051001111023.X proposes a kind of roller tray type friction type stepless speed changer, its gear shift mode
It is：Do not change intermediate roller position, only change gear ratio by changing the angle excursion of intermediate roller, that is, gear ratio size with
Angle of deviation is relevant.But when intermediate roller deflection, it will be inconsistent because of contact point velocity attitude with driven wheel contact position
And produce relative velocity and skimming wear lateral, and then affect transmission efficiency.Therefore, this gear shift mode is also not suitable for taking relatively
Big coefficient of friction, its bearing capacity is inevitable very low.
Content of the invention
The technical problem to be solved is to provide for a kind of structure simply, low cost, and speed adjusting gear operation is light
There is the frictional variable speed device that double intermediate rollers turn to diameter changing mechanisms.
In order to solve above technical problem, the invention provides a kind of have rubbing of double intermediate rollers steering diameter changing mechanism
Erasing stepless speed change device, including input shaft, input shaft gear, input frictional disk, jackshaft, micro-machine, motor cabinet, first
Intermediate roller, the first roller shaft, the second intermediate roller, the second jackshaft, stub, reducing support, output frictional disk and output shaft.
Input shaft gear is fixed on input shaft, both no relative motioies, and input shaft is connected with gantry rotation pair, therefore inputs
Shaft gear and input shaft only can be rotated around the axis of input shaft with identical angular velocity；Input frictional disk is fixed on jackshaft,
Both no relative motioies, jackshaft is connected with gantry rotation pair, therefore inputs frictional disk and jackshaft only can be with identical angular velocity
Axis around jackshaft rotates；The processing of input frictional disk side is with teeth, engages with input shaft gear.
First intermediate roller, the second intermediate roller and the first roller shaft, the second roller shaft are connected with rotating pair respectively, and first
It is moving sets between roller shaft, the second roller shaft and stub to be connected, mutually compress between two-wheeled, achievable frictional drive, two
Size of wheel is identical, and gear ratio is 1；Meanwhile, the first intermediate roller and input frictional disk mutually compress, and are that friction pair connects, can be real
Existing frictional drive；Second intermediate roller and output frictional disk also mutually compress, and are that friction pair connects, achievable frictional drive.
Stub and reducing support are to rotate secondary connection, and stub only can be around own axis relative to reducing support；Small-sized
Motor is arranged on motor cabinet, and motor cabinet and reducing support are affixed, and motor output shaft and stub are affixed, both deads in line, becomes
Footpath support and frame are connected by moving sets.
Output frictional disk is fixed on output shaft, both no relative motioies, and output shaft and frame are after mechanism's compression for turning
Dynamic secondary connection, therefore output frictional disk and output shaft only can be rotated around the axis of output shaft with identical angular velocity.
During deceleration transmission, power is inputted by input shaft, is transferred to the first intermediate roller via input frictional disk, in second
Between roller, finally by output frictional disk export output shaft；During step-up drive, power transfer path is contrary.
When needing to adjust gear ratio, all of stub is synchronously driven smoothly to turn over phase in the same direction by micro-machine
Same angle, then can drive intermediate roller to produce lateral deviation accordingly, and due to side drift angle very little, micro-machine is without the too many work(of consumption
Rate, resistance is also little.Assume that now the first intermediate roller and the contact point of input frictional disk are p1, the speed of p1 point is Vp1, the
It is pure rolling between one intermediate roller and input frictional disk, then on the first intermediate roller, the speed of p1 point is also Vp1, in first
Between on roller the speed of p1 point can be understood as a sum velocity, be made up of two parts：One is the middle rolling with respect to first of p1 point
Velocity of rotation Vr1 of the pivot center of wheel, its direction is perpendicular to the pivot center of the first intermediate roller；Two is the first intermediate roller
Overall translational velocity Vs1.Also it is to determine due to the direction of the presence Vs1 of guiding mechanism, and have Vp1=Vr1+Vs1, first
Intermediate roller can along input frictional disk radial direction with speed Vs1 move, similarly, in the second intermediate roller and output
There is also a contact point p2 between frictional disk, the second intermediate roller can be obtained by the direction of motion and Vector modulation relation and also can
Center towards output frictional disk is moved with speed Vs2, is understood in the middle of the first intermediate roller and second by analyzing the direction of Vs2
The direction of motion of roller is consistent.When the first intermediate roller and the second intermediate roller move to a conjunction along the direction of guiding mechanism
During the position of reason, motor is just returned, now Vs1=Vs2=0, reach a new drive position, realize the change of gear ratio.Turn to
After motor just returns, intermediate roller reaches new driving contact radial location, and now motor is locked out（Lockable mechanism can take electromagnetism
The modes such as mode of braking, in figure is not drawn into）, to ensure that gear ratio is in steady statue.
In the present invention, in order to ensure the first intermediate roller and the second intermediate roller, the first intermediate roller and input friction
Enough normal pressures are had, whole mechanism needs to compress, compression on friction pair between disk, the second intermediate roller and output frictional disk
Power can act on output frictional disk on, direction upwards it is also possible to act on by input shaft, input shaft gear, input frictional disk,
On the input assembly of jackshaft composition, direction is downward.
In the present invention, in order that stable transmission and uniform stressed, intermediate transmission turns to diameter changing mechanism, including input friction
Disk, jackshaft, micro-machine, motor cabinet, the first intermediate roller, the second intermediate roller, stub, reducing support, have 2 sets, right
Claim to be distributed in the both sides of output frictional disk.As long as the middle diameter changing mechanism that turns to can be symmetrically distributed in around output frictional disk,
Can there are many sets in theory, but many sets turn to diameter changing mechanism when executing speed governing it is necessary to be Complete Synchronization, implementation is permissible
It is motor or the mechanical type synchronous steering mechanism of Synchronization Control, the parallelogram connection-rod that can be for example 1 using gear ratio
Mechanism or synchronous belt drive mechanism etc.（In figure is the motor of Synchronization Control）To keep synchronous, but to be because the manufacture of intermediate roller
Deviation, or the abrasion inequality causing because of system discontinuity, it is difficult to ensure that many sets turn to reducing in mechanism's actual motion
The Complete Synchronization of reducing between mechanism, its solution can be to ensure that from structure cover turns to change more by specific mechanism
The Complete Synchronization of motion between the mechanism of footpath, or revised between many set steering diameter changing mechanisms using motor is carried out with closed loop control
The kinematic error of motion, covers the organization plan turning to diameter changing mechanism more, and only a set of intermediate transmission turns to the side of diameter changing mechanism
Case, and ensure two kinds of basic skills of synchronicity between Duo Tao mechanism, all within the protection domain of patent of the present invention.
The present invention proposes a kind of frictional variable speed device with double intermediate rollers steering diameter changing mechanisms, can control
Great friction coefficient drive contact radius carry out smoothing under the conditions of lower resistance, low abrasion, continuously change, and have structure letter
The advantages of single, infinitely variable speeds manipulate light.
Superior effect of the present invention is：
1. control great friction coefficient drive contact radius to carry out smoothing under the conditions of lower resistance, low abrasion, continuously become
Change, structure is simple, infinitely variable speeds manipulate light；
2., when need carry out speed governing, change the friction that drive effective CONTACT WITH FRICTION radius is realized overcoming needed for infinitely variable speeds
Resistance is little, and steering diameter changing mechanism operation is light, and the abrasion causing is little；
3. do not need during speed governing to disconnect power transmission；
4. the function of commutating can be realized.
Brief description
Fig. 1 is the principle schematic diagram. of the present invention；
Fig. 2 and Fig. 3 is the speed control principle schematic diagram of the present invention；
In figure label declaration：
0- frame；
1- input shaft；2- input shaft gear；
3- inputs frictional disk；4- jackshaft；
5- micro-machine；6- motor cabinet；
7- first intermediate roller；8- first roller shaft；
9- second roller shaft；10- second intermediate roller；
11- stub；12- reducing support；
13- exports frictional disk；14- output shaft.
Specific embodiment
Refer to shown in accompanying drawing, the invention will be further described.
As shown in figure 1, the invention provides a kind of have the frictional variable speed that double intermediate rollers turn to diameter changing mechanism
Device, including rolling in the middle of input shaft 1, input shaft gear 2, input frictional disk 3, jackshaft 4, micro-machine 5, motor cabinet 6, first
Wheel the 7, first roller shaft 8, the second roller shaft 9, the second intermediate roller 10, stub 11, reducing support 12, output frictional disk 13 and defeated
Shaft 14.
Specific kinematic pair relation is as follows：
Input shaft gear 2 is fixed on input shaft 1, both no relative motioies, and input shaft 1 rotates pair with frame 0 and is connected, defeated
Enter shaft gear 2 and input shaft 1 only can be rotated around the axis of input shaft 1 with identical angular velocity；Input frictional disk 3 is fixed in centre
On axle 4, both no relative motioies, jackshaft 4 rotates pair with frame 0 and is connected, and inputting frictional disk 3 only can be identical with jackshaft 4
Angular velocity around jackshaft 4 axis rotate；The processing of input frictional disk 3 side is with teeth, engages with input shaft gear 2；
First intermediate roller 7, the second intermediate roller 10 and the first roller shaft 8, the second roller shaft 9 are respectively to rotate secondary company
Connect, be moving sets between the first roller shaft 8, the second roller shaft 9 and stub 11 and be connected, mutually compress between two-wheeled, can achieve
Frictional drive, two-wheeled is equivalently-sized, and gear ratio is 1；Meanwhile, the first intermediate roller 7 and input frictional disk 3 mutually compress, for rubbing
Wipe secondary connection, achievable frictional drive；Second intermediate roller 10 and output frictional disk 13 also mutually compress, and are that friction pair connects,
Achievable frictional drive.
Stub 11 and reducing support 12 are to rotate secondary connection, and stub 11 reducing support 12 relatively only can turn around own axes
Dynamic；Micro-machine is arranged on motor cabinet 6, and motor cabinet 6 and reducing support 12 are fixed together, and motor output shaft and stub 11 are solid
Connect, both deads in line, reducing support 12 and frame 0 connect for moving sets.
Output frictional disk 13 is affixed on the output shaft 14, both no relative motioies, and output shaft 14 is compressed in mechanism with frame 0
It is to rotate secondary connection afterwards, therefore output frictional disk 13 and output shaft 14 only can be turned around the axis of output shaft 14 with identical angular velocity
Dynamic.
During deceleration transmission, power is inputted by input shaft it is assumed that the rotating speed of input shaft 1 is, the number of teeth of input shaft gear 2
For, on input frictional disk 3, the number of teeth of the tooth of processing is, then input the axis around jackshaft 4 for the frictional disk 3 rotating speed be
Assume that the first intermediate roller 7 with the contact point of input frictional disk 3 apart from the distance of jackshaft 4 axis is, in second
Between the contact point of roller 10 and output frictional disk 13 apart from the distance of output shaft 14 axis beIt is contemplated that two intermediate rollers
Between gear ratio be 1 it is assumed that the rotating speed of output shaft 14 is, have, and the rotation of input shaft 1 and output shaft 14
In opposite direction, then speed reducing ratio is：
；
If we assume that the radius of input frictional disk 3 is, output frictional disk 13 radius be, andIf another
, then, and have
；；
Because reducing support 12 and frame connect for moving sets, therefore x is continually varying.The tooth of wherein input shaft gear 2
On number and input frictional disk 3, the ratio of the number of teeth of tooth of processing is definite value, and the ratio r1/r2 of centre-to-centre spacing is continually varying, therefore can
To realize infinite speed reduction.And the excursion of gear ratio is
；
It is found that mechanism can achieve commutation function within the specific limits.
When power inputs from outfan, this mechanism can realize stepless speedup；
2 elaborate speed control principle below in conjunction with the accompanying drawings：
When gear ratio will be changed it is assumed that the stub by the synchronous drive both sides of micro-machine 5 is counterclockwise smoothly along axis
Turn over oneAngle, then intermediate roller 7,10 can be driven accordingly to rotate, the top view of result is as shown in Figure 2（Assume master
Pin 11 from two-wheeled plane enough close to）, the first intermediate roller 7 is in the lower section of input frictional disk 3, therefore is represented by dotted lines：
Assume that the first intermediate roller 7 is p1 with the contact point of input frictional disk 3, input frictional disk 3 turns according to direction as shown
Dynamic, then the speed of p1 point is Vp1 it is assumed that being pure rolling between the first intermediate roller 7 and input frictional disk 3, then in the middle of first
On roller 7, the speed of p1 point is also Vp1, and on the first intermediate roller 7, the speed of p1 point can be understood as a sum velocity, is by two
Part composition, one is velocity of rotation Vr1 of the pivot center that p1 point is with respect to the first intermediate roller 7, and direction is perpendicular to first
The pivot center of intermediate roller 7, two is translational velocity Vs1 of the first intermediate roller 7 entirety, due to the presence Vs1 of guiding mechanism
Direction be also to determine and there is Vp1=Vr1+V1s such vector correlation formula, by being not difficult to find out the first intermediate roller 7 in Fig. 2
Can be moved towards the center of input frictional disk 3 with the speed of a Vs1, similarly, in dynamic intermediate roller 10 and output frictional disk
There is also a contact point p2 between 13, be not difficult to find out the according to the direction of motion and Vector modulation relation of diagram in figure 3
Two intermediate rollers 10 also can be moved towards the center of output frictional disk 13 with the speed of a Vs2, and upper and lower motion is consistent.
When upper and lower intermediate roller moves to a rational position along the direction of guiding mechanism by motor return just so thatIt is zero,
Vs1=Vs2=0 so now, reaches a new drive position, realizes the change of gear ratio.After steer motor is just returned, middle
Roller reaches new driving contact radial location, and now motor is locked out（Lockable mechanism can take the modes such as electromagnetic braking mode,
In figure is not drawn into）, to ensure that gear ratio is in steady statue.
Claims (1)
1. a kind of steering reducing stepless speed changing mechanism with double intermediate rollers, including in input shaft, jackshaft, stub, first
Between roller, the second intermediate roller and output shaft it is characterised in that：Described first intermediate roller and the second intermediate roller employ one
To the intermediate roller having viscous-elastic behaviour, make intermediate roller produce lateral deviation, make intermediate roller change its footpath in the presence of side force
To position, realize the regulation of speed ratio；
Wherein, described input shaft is connected with input shaft gear, both no relative motioies, input shaft is connected with gantry rotation pair,
Input shaft gear and input shaft are only rotated around the axis of input shaft with identical angular velocity；Input frictional disk is fixed in jackshaft
On, both no relative motioies, jackshaft is connected with gantry rotation pair, therefore inputs frictional disk and jackshaft only with identical angular velocity
Axis around jackshaft rotates；The processing of input frictional disk side is with teeth, engages with input shaft gear；
Described first intermediate roller, the second intermediate roller and the first roller shaft, the second roller shaft are connected with rotating pair respectively, and first
It is moving sets between roller shaft, the second roller shaft and stub to be connected, mutually compresses between two-wheeled, realize frictional drive, two-wheeled
Equivalently-sized, gear ratio is 1；Described first intermediate roller and input frictional disk mutually compress, and are that friction pair connects, realize friction
Transmission；Second intermediate roller and output frictional disk also mutually compress, and are that friction pair connects, realize frictional drive；
Described stub and reducing support are to rotate secondary connection, and stub is relative to reducing support only about own axis；Reducing support
Affixed with motor cabinet, motor cabinet is provided with micro-machine, motor output shaft and stub are affixed, both deads in line, and reducing props up
Frame and frame are connected by moving sets；
Output frictional disk is connected with described output shaft, both no relative motioies, output shaft and frame are after mechanism's compression for turning
Dynamic secondary connection, therefore output frictional disk and output shaft are only rotated around the axis of output shaft with identical angular velocity.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201310480738.8A CN103542058B (en) | 2013-10-15 | 2013-10-15 | Frictional infinitely variable speed device with double-intermediate-roller steering reducing mechanism |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201310480738.8A CN103542058B (en) | 2013-10-15 | 2013-10-15 | Frictional infinitely variable speed device with double-intermediate-roller steering reducing mechanism |
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| CN103542058A CN103542058A (en) | 2014-01-29 |
| CN103542058B true CN103542058B (en) | 2017-02-15 |
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Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105179630B (en) * | 2015-09-17 | 2017-11-03 | 王吉 | A kind of link lever type stepless speed changer of pulse free |
| CN106567915A (en) * | 2016-05-06 | 2017-04-19 | 莫韬 | Steering double-roller flat plate infinitely variable speed transmission device |
Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| BE416624A (en) * | ||||
| US1738965A (en) * | 1928-01-02 | 1929-12-10 | Reina Gian Battista | Variable-speed transmission |
| FR2241216A5 (en) * | 1973-08-16 | 1975-03-14 | Virlon Jean Claude | Speed varying device for general use - is for automobiles, machine tools etc. and has two discs separated by rollers |
| DE3236693A1 (en) * | 1981-10-08 | 1983-05-26 | Tektronix, Inc., 97077 Beaverton, Oreg. | SYSTEM FOR STORING AND VISIBLE WAVE SHAPES |
| WO1992022759A1 (en) * | 1991-06-13 | 1992-12-23 | Dong Hwi Lee | Rotary to stepless motion converter |
| CN1439821A (en) * | 2003-02-23 | 2003-09-03 | 崔光彩 | Roller and disc stepless gear |
| WO2012151615A1 (en) * | 2011-05-06 | 2012-11-15 | Durack Michael | Toroidal variable speed traction drive |
| CN102808909A (en) * | 2011-06-03 | 2012-12-05 | 袁啸宇 | Non-slip type stepless speed change device |
| CN102927225A (en) * | 2011-08-10 | 2013-02-13 | 北汽福田汽车股份有限公司 | Stepless speed change mechanism and automobile |
-
2013
- 2013-10-15 CN CN201310480738.8A patent/CN103542058B/en active Active
Patent Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| BE416624A (en) * | ||||
| US1738965A (en) * | 1928-01-02 | 1929-12-10 | Reina Gian Battista | Variable-speed transmission |
| FR2241216A5 (en) * | 1973-08-16 | 1975-03-14 | Virlon Jean Claude | Speed varying device for general use - is for automobiles, machine tools etc. and has two discs separated by rollers |
| DE3236693A1 (en) * | 1981-10-08 | 1983-05-26 | Tektronix, Inc., 97077 Beaverton, Oreg. | SYSTEM FOR STORING AND VISIBLE WAVE SHAPES |
| WO1992022759A1 (en) * | 1991-06-13 | 1992-12-23 | Dong Hwi Lee | Rotary to stepless motion converter |
| CN1439821A (en) * | 2003-02-23 | 2003-09-03 | 崔光彩 | Roller and disc stepless gear |
| WO2012151615A1 (en) * | 2011-05-06 | 2012-11-15 | Durack Michael | Toroidal variable speed traction drive |
| CN102808909A (en) * | 2011-06-03 | 2012-12-05 | 袁啸宇 | Non-slip type stepless speed change device |
| CN102927225A (en) * | 2011-08-10 | 2013-02-13 | 北汽福田汽车股份有限公司 | Stepless speed change mechanism and automobile |
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|---|---|
| CN103542058A (en) | 2014-01-29 |
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